EP0567736B1 - Moteur hydrostatique avec un dispositif de freinage - Google Patents

Moteur hydrostatique avec un dispositif de freinage Download PDF

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Publication number
EP0567736B1
EP0567736B1 EP93103001A EP93103001A EP0567736B1 EP 0567736 B1 EP0567736 B1 EP 0567736B1 EP 93103001 A EP93103001 A EP 93103001A EP 93103001 A EP93103001 A EP 93103001A EP 0567736 B1 EP0567736 B1 EP 0567736B1
Authority
EP
European Patent Office
Prior art keywords
brake
pressure
hydrostatic motor
motor according
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93103001A
Other languages
German (de)
English (en)
Other versions
EP0567736A1 (fr
Inventor
Rainer Stoelzer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0567736A1 publication Critical patent/EP0567736A1/fr
Application granted granted Critical
Publication of EP0567736B1 publication Critical patent/EP0567736B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control

Definitions

  • the invention relates to a hydrostatic motor with a braking device according to the preamble of claim 1.
  • Hydrostatic motors of this type are used in particular as so-called plug-in motors for installation in, for example, wheel hubs of vehicle drive wheels.
  • a further reduction in the axial length of the hydrostatic motor can be achieved by arranging the compression spring in an axial material bore in the pressure element.
  • the length of the compression spring in the tensioned state when the brake is released is essentially equal to the length dimension of the axial blind bore.
  • one of the two brake surfaces can be formed, for example, on the housing and the other on a brake disk axially displaceably fastened to the rotor, two brake disks are provided according to a development of the invention, the surfaces of which face one another are the brake surfaces.
  • the hydrostatic motor shown schematically in FIG. 1 is intended for installation in the hub of a wheel for the purpose of driving the same and is designed as an axial piston motor in a swashplate construction with a constant displacement volume. It comprises in a conventional manner a substantially cylindrical and one-sided open housing 1, a connecting plate 2 with a suction and a pressure connection (both not shown) which can be releasably closed off the open end of the same, one by means of cones 3, 4 in the housing 1 and in the Connection plate 2 rotatably mounted output shaft 5, a rotatably arranged on this rotor in the form of a cylinder drum 6, which is supported on a control plate attached to the connection plate 2 (not shown), a swash plate 7 attached to the control disc on the housing 1 and a braking device to be described 8.
  • An annular space 9 is formed between housing 1 and cylinder drum 6.
  • axially extending and evenly distributed over the circumference cylindrical bores 10 are formed in a known manner, which open via cylinder channels 11 on the end face of the cylinder drum 6 facing the control disc.
  • two diametrically opposed control kidneys are formed in a known manner, which produce the connection between the cylinder channels 11 and the suction and the pressure connection when the cylinder drum 6 rotates.
  • Pistons 12, which are displaceably guided in the cylinder bores 10, are supported with their piston ends opposite the cylinder channels 11 by sliding shoes 13 on the swash plate 7.
  • the housing 1 is provided at its open end facing the connection plate 2 with a circumferential, radially outwardly extending housing flange part 14, in which the annular space 9 is expanded radially outwards.
  • the enlarged annulus area formed in this way is over a encircling radial shoulder 15 formed on the housing 1 is connected to the remaining annular area and is stepped twice by a second radial shoulder 16 and a third radial shoulder 17 and thereby divided into three areas of different outside diameters; the largest outside diameter area opens out on the end face of the housing 1 facing the connection plate 2.
  • the braking device 8 is arranged in the enlarged annulus area. It comprises a brake disk package consisting of a first and a second, each annular brake disk 18 or 19, an annular pressure element 20, a plurality of compression springs 21 and a pressure line 22 for a hydraulic pressure medium.
  • the first and the second brake disks 18, 19 are by means of nose-shaped projections 23 (see FIG. 2) and 24 (see FIG. 1), each with an axial toothing in the housing inner wall 25 or the outer surface of the cylinder drum 6 in the area between the first and second shoulder 15, 16 axially displaceable and rotatably arranged. Only the toothing for the first brake disk 18, which is formed in the housing inner wall 25 and is designated by the reference numeral 26, is shown (see FIG. 2).
  • the second brake disk 19 faces the first shoulder 15 and is supported by the latter during the brake intervention with the first brake disk 18, which is still to be described.
  • the first shoulder 15 and the surface of the first brake disk 19 facing it are essentially free of friction.
  • the pressure element 20 is in the expanded annular space on the housing 1 rotatably and axially displaceable with the stroke A and for this purpose has an axial dimension which is correspondingly smaller than the axial distance between the end face of the housing 1 or the connecting plate 2 and the first Shoulder 15 minus the axial dimensions of both brake disks 18,19.
  • the pressure element 20 also has in its outer lateral surface a circumferential, radially extending step 27, which is assigned to the third shoulder 17 and is axially spaced from it in every axial position of the pressure element 20. In this way, the third shoulder 17 and the step 27 define an annular first pressure space 28.
  • the stage 27 divides the pressure element 20 into a section of smaller and a section of larger outside diameter.
  • the latter section is guided on the housing inner wall 25 in the region between the shoulder 17 and the end face of the housing 1 during the axial displacement of the pressure element 20.
  • An annular seal 29 is arranged in a circumferential groove in the outer circumferential surface of the pressure element 20.
  • the smaller outside diameter of the pressure element 20 is somewhat smaller than the outside diameter of the annular space area between the first and second shoulders 15, 16.
  • the axially extending annular gap 30 formed in this way between the housing inner wall 25 in the region between the second and third shoulders 16, 17 and the pressure element section of smaller outer diameter represents a second pressure chamber which is in communication with the first pressure chamber 28 and with it forms a common pressure chamber 28,30.
  • An annular body 32 with play and an annular seal 31 are arranged in the annular gap 30. The latter partially protrudes into the pressure chamber 28 and is supported via the ring body 32 on the second shoulder 16 serving as an abutment.
  • the compression springs 21 are designed as cylindrical helical springs and are integrated in the pressure element 20; for this purpose they are inserted in axially extending blind bores 33 in the pressure element 20 and are supported with a prestress on the connection plate 2; their length when the brake disks 18, 19 have been released from the brake (see FIG. 4) is equal to the length dimension of the axial blind bores 33.
  • the latter are arranged at equal mutual distances on a pitch circle.
  • the pressure line 22 is formed in the area between two adjacent axial blind bores 33 as a through bore which runs axially through the pressure element 20 and opens out at the step 27.
  • a connecting line 34 running axially through the connecting plate 2 (see FIG. 1) is aligned with the pressure line 22.
  • the mutually facing end regions of both lines 22, 34 have a larger diameter than the remaining line regions and are connected to them via a circumferential, radial shoulder connected. Only the one located in the pressure line 22 with the Paragraph designated 35 is shown (see FIG. 2).
  • a lock-up clutch 36 is inserted with play into the line end regions of larger diameter and establishes a connection between the two lines 22, 34.
  • the lock-up clutch 36 is shorter by the dimension B than the two line sections of larger diameter.
  • the dimension B is somewhat larger than the stroke A of the pressure element 20.
  • the connecting line is connected in a manner not shown to the pressure medium circuit of the hydrostatic motor or a pressure medium line connected to it.
  • the function of the above-described hydrostatic motor is described below with reference to the braking device according to the invention:
  • the compression springs 21 constantly press the pressure element 20 in the direction of the brake disc package 18, 19.
  • the pressure element 20 is in the (left) braking position shown in FIGS. 2 and 3, in which it presses the two brake disks 18, 19 against the first shoulder 15 serving as support and thus holding each other in braking.
  • the pressure element 20 is arranged at a distance B corresponding to the stroke A from the connection plate 2 and the bridging bush 36 from the shoulder 35 in the pressure line 22.
  • the compression springs 21 move the pressure element 20 back into the braking position shown in FIGS Shoulder 15 are supported. Because of its rotationally fixed arrangement on the housing 1, the first brake disk 18 is at rest relative to the pressure element 20 even when the cylinder drum 6 is rotating, so that the latter does not absorb any braking torque when the cylinder drum 6 is braked.
  • the pressure chamber 28, 30 can be supplied with hydraulic pressure medium via more than one pressure line 22. Furthermore, it is possible to arrange the second brake disk 19 on the housing 1 in a manner fixed against relative rotation and optionally axially immovable; in this case, the first brake disk 18 is to be fastened to the cylinder drum 6 in an axially displaceable manner. Instead of a loosely inserted ring body 32, it is possible to design the same as part of the housing 1. With a sufficiently stable design of the second brake disc 19, the first shoulder 15 can be omitted. It is also conceivable to design the brake disc package with more than two brake discs.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)
  • Hydraulic Motors (AREA)

Claims (12)

  1. Moteur hydrostatique comprenant un rotor (6) monté tournant dans un carter (1) et un dispositif de freinage (8), placé dans un espace annulaire (9), entre le carter (1) et le rotor (6), qui comprend au moins deux surfaces de freinage (18, 19) maintenues solidaires en rotation respectivement sur le carter (1) et sur le rotor (6), dont l'une au moins est déplaçable dans la direction axiale du moteur hydrostatique, avec au moins une conduite de pression (22) pour un fluide hydraulique, sous pression, avec un élément de pression (20) pouvant coulisser axialement, qui présente une surface de pression pouvant être alimentée avec le fluide hydraulique sous pression et délimitant une chambre de pression (28, 30), et au moins un ressort de pression (21) agissant sur l'élément de pression (20) en direction de la surface de freinage (18, 19) déplaçable, la surface de freinage (18, 19) déplaçable étant maintenue par l'élément de pression (20), en cas de décharge hydraulique de celui-ci, en engagement de freinage avec l'autre surface de freinage (19) et pouvant être libérée de l'engagement de freinage, par coulissement axial de l'élément de pression (20) sous l'effet de la force du fluide hydraulique sous pression, caractérisé en ce que la conduite de pression (22) s'étend axialement à travers l'élément de pression (20), jusqu'à hauteur de la surface de pression (27), et en ce que la chambre de pression (28, 30) comprend une fente annulaire (30) s'étendant axialement entre l'élément de pression (20) et le carter (1), et s'étend dans la fente annulaire (30) jusqu'à un corps annulaire (32) déplaçable par rapport à l'élément de pression (20).
  2. Moteur hydrostatique selon la revendication 1, caractérisé par deux disques de frein (18, 19) dont les surfaces tournées l'une vers l'autre sont les surfaces de freinage.
  3. Moteur hydrostatique selon la revendication 2, caractérisé par un appui (15) côté carter, contre lequel prennent appui les disques de frein (18, 19) pendant leur engagement de freinage.
  4. Moteur hydrostatique selon la revendication 2 ou 3, caractérisé en ce que les disques de frein (18, 19) peuvent coulisser axialement.
  5. Moteur hydrostatique selon la revendication 3 ou 4, caractérisé en ce que les surfaces tournées l'une vers l'autre de l'appui (15) et du disque de frein (19) voisin sont sensiblement sans friction.
  6. Moteur hydrostatique selon l'une au moins des revendications 2 à 5, caractérisé en ce que l'élément de pression (20) et le disque de frein (18) qui lui est voisin, sont placés solidaires en rotation sur le carter (1).
  7. Moteur hydrostatique selon l'une au moins des revendications précédentes, caractérisé en ce qu'une étanchéité (31) est placée dans la fente annulaire (30).
  8. Moteur hydrostatique selon l'une au moins des revendications précédentes, caractérisé en ce que le corps annulaire (32) est placé librement dans la fente annulaire (30) et peut prendre appui contre une butée (16) côté carter.
  9. Moteur hydrostatique selon l'une au moins des revendications précédentes, caractérisé en ce que l'élément de pression (20) présente un trou borgne (33) axial dans lequel est placé le ressort de pression (21).
  10. Moteur hydrostatique selon la revendication 9, caractérisé en ce qu'à l'état tendu, avec engagement de freinage supprimé, la longueur du ressort de pression (21) est sensiblement égale à la dimension de longueur du trou borgne (33) axial.
  11. Moteur hydrostatique selon l'une au moins des revendications précédentes, caractérisé en ce que le ressort de pression (21) prend appui contre une plaque de raccord (2) fixée amovible sur le carter (1).
  12. Moteur hydrotatique selon la revendication 11, caractérisé par une conduite de raccord (34) s'étendant à travers la plaque de raccord (2), alignée avec la conduite de pression (22), et par une douille de pontage (36), qui réalise une liaison entre les deux conduites (22, 34).
EP93103001A 1992-04-30 1993-02-25 Moteur hydrostatique avec un dispositif de freinage Expired - Lifetime EP0567736B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4214397 1992-04-30
DE4214397A DE4214397C2 (de) 1992-04-30 1992-04-30 Hydrostatischer Motor mit einer Bremseinrichtung

Publications (2)

Publication Number Publication Date
EP0567736A1 EP0567736A1 (fr) 1993-11-03
EP0567736B1 true EP0567736B1 (fr) 1996-03-20

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EP93103001A Expired - Lifetime EP0567736B1 (fr) 1992-04-30 1993-02-25 Moteur hydrostatique avec un dispositif de freinage

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EP (1) EP0567736B1 (fr)
DE (2) DE4214397C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9249664B2 (en) 2012-04-24 2016-02-02 Komatsu Ltd. Bent axis type axial piston motor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08177899A (ja) * 1994-12-27 1996-07-12 Komatsu Ltd 油圧モータのブレーキ装置
DE10112501B4 (de) * 2001-03-15 2015-11-12 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Antriebseinheit
DE102006025969A1 (de) * 2006-06-02 2007-12-06 Robert Bosch Gmbh Hydrostatische Kolbenmaschine und Druckring für eine Bremseinrichtung derselben
DE102011076581A1 (de) 2010-12-23 2012-06-28 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Bremsvorrichtung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1086190B (de) * 1958-08-01 1960-07-28 Kaemper Motoren G M B H Bremsvorrichtung fuer hydraulische Motoren
DE2130513A1 (de) * 1971-06-19 1972-12-21 Linde Ag Axialkolbenmaschine mit einer Schraegscheibe
DE2931641A1 (de) * 1979-08-01 1981-02-05 Mannesmann Ag Hydrostatischer axialkolbenmotor in schraegachsenbauweise, insbesondere fuer fahrgetriebe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9249664B2 (en) 2012-04-24 2016-02-02 Komatsu Ltd. Bent axis type axial piston motor

Also Published As

Publication number Publication date
EP0567736A1 (fr) 1993-11-03
DE4214397C2 (de) 1995-07-06
DE59301926D1 (de) 1996-04-25
DE4214397A1 (de) 1993-11-04

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